Hydrolager

Abstract

Hydraulic bearing (10), in particular a radially damping hydraulic bearing, comprising a bearing core (30), an outer sleeve (20) and a spring element (40) made of elastomeric material, which materially encompasses at least some of the bearing core (30) and is arranged between the bearing core (30) and the outer sleeve (20), wherein the hydraulic bearing (10) also comprises a support structure (50) formed by a first support ring (51) and a second support ring (52), as well as by two half-shells (53, 54) arranged between the first and second support rings (51, 52), wherein the hydraulic bearing (10) comprises at least a first fluid chamber (61) and a second fluid chamber (62) which are bounded by the spring element (40), the half-shells (53, 54) and / or the outer sleeve (20) and the bearing core (30), wherein the spring element (40) comprises at least one intermediate membrane (41) which is arranged between the first and second fluid chambers (61, 62),wherein the at least one intermediate membrane (41) has a membrane head (42) by means of which it is fixed to the support structure (50) in such a way that the membrane head (42) is arranged with or without play in a form-fitting manner in a receptacle (70) formed by the half-shells (53, 54), characterized in that the maximum thickness (Dk) of the membrane head (42) is greater than the maximum thickness (Dm) of the intermediate membrane (41).

Description

The invention relates to a hydraulic bearing according to the preamble of claim 1.Hydraulic bearings, in particular also radial damping hydraulic bearings, are generally known. They are used, for example, for the storage of chassis components. Dynamic force components occurring there, for example, during braking and acceleration should be damped as much as possible.For example, DE 10 2008 058 239 B4 discloses a radially damping hydraulic mount. In this hydraulic bearing, a bearing core is surrounded by a spring body made of elastomer material and is arranged in an outer sleeve. The spring body is held in the outer sleeve by a cage structure which has a ring on each of the end faces which holds the spring body. The spring body consists of at least two membranes arranged between the two rings and the core, as well as two intermediate membranes. The two rings are connected to one another via webs, wherein the webs serve to ensure the necessary distance between the two rings and to form a connecting surface on the inside for the two intermediate membranes. Rings and webs together form a support cage. Two fluid chambers are formed between the outer sleeve, the core and the spring body. The fluid contained therein serves for the radial damping of dynamic movements of the bearing core in a critical frequency range. The two fluid chambers are each separated from one another by an intermediate diaphragm which extends from the bearing core to the web of the cage structure. The intermediate membrane is vulcanized onto both the bearing core and the web of the cage structure. In order to prevent the bearing from bursting during highly dynamic movements of the bearing core and to be able to achieve a pressure compensation between the two fluid chambers necessary for this, two valves are provided. The valves are designed as ramp valves which are vulcanized onto the webs on the outside in the extension of the intermediate membrane and extend between the webs and the outer sleeve. If the bearing core moves dynamically, the pressure in one of the two fluid chambers rises or falls in each case and, depending on the pressure ratio, the valve flap opens or closes above a critical pressure.It is problematic with this construction that valves, webs and intermediate membrane are arranged in series from the inside to the outside and compete with each other for the limited available radial installation space. With respect to the limited installation space of the valve, the opening cross section of the valve is therefore limited. This results in a limitation of the degradation of high pressures. With respect to the intermediate membranes, the radial installation space limitation leads to short clamped intermediate membrane lengths in the radial direction. Short intermediate membrane lengths lead to high expansions due to dynamic loads and thus to a short service life of the intermediate membranes.DE 10 2006 052 918 A1 discloses an axially prestressed hydraulic bearing. It is proposed here that the bearing has an inner part and an outer sleeve, and a cage device which is connected to the inner part via elastomer support springs. Between the inner part and the outer sleeve, at least two liquid chambers are formed which are connected via at least one channel. In order to avoid loading of the liquid chamber during operation, it is proposed that at least one liquid chamber formed with the elastomer support spring has an extension component in the axial direction and that the bearing is axially prestressed.DE 10 2007 026 469 A1 discloses a modular elastomer bearing with hydraulic damping. The bearing has a metallic inner part, an outer sleeve and an elastomeric bearing body between the inner part and the outer sleeve, which body has at least one reinforcing element vulcanized in. At least two chambers are present for receiving a fluid damping means, between which at least one web extends from the inner part in the direction of the outer sleeve. The webs are part of a web module which additionally comprises the inner part of the bearing and can be connected in a form-fitting manner to an outer hydro module.The object is therefore to provide an improved, radially damping hydraulic mount which enables the highest possible damping with at the same time a long service life of the intermediate membranes. In particular, a high radial expansion lengths for the intermediate membranes, which are arranged between the fluid chambers, should be made possible, so that relatively lower expansions are induced in the intermediate membrane when these intermediate membranes bulge due to the differential pressures occurring between the chambers. The hydraulic bearing should have as few components as possible and be realizable as simply and cost-effectively as possible.Main features of the invention are set out in the characterizing part of claim 1. Embodiments are the subject matter of claims 2 to 09.In a hydraulic bearing, in particular in a radially damping hydraulic bearing, having a bearing core, an outer sleeve and having a spring body made of elastomer material, which spring body comprises the bearing core in a materially bonded manner at least in regions and is arranged between the bearing core and the outer sleeve, wherein the hydraulic bearing additionally has a supporting structure which is formed by a first supporting ring and a second supporting ring, and by two half shells arranged between the first and second supporting rings, wherein the hydraulic bearing has at least one first fluid chamber and one second fluid chamber which are bounded by the spring body, the half shells and / or the outer sleeve and the core, wherein the spring body has at least one intermediate membrane which is arranged between the first and the second fluid chamber, the invention proposes that at least one intermediate membrane has a membrane head, with the aid of which it is fixed to the supporting structure, specifically in such a way that, the diaphragm head is positively arranged with or without play in a receptacle which is formed by the half shells, and the maximum thickness of the diaphragm head is greater than the maximum thickness of the intermediate diaphragm.The bearing core of the hydraulic bearing is designed to receive a fastening element or to form such a fastening element. For this purpose, the bearing core can have, for example, an inner bore or transition into a threaded pin. The bearing core is at least partially arranged in the outer sleeve. The outer sleeve is preferably cylindrical. It accommodates all other components. The outer sleeve is substantially in the form of a cylindrical tube having a first end face formed at the first end of the tube and a second end face formed at the second end of the tube diametrically opposite the first end. The end faces are each open, so that the tube is hollow cylindrical. In this way, the bearing core, the spring body and the supporting structure can be easily inserted into the outer sleeve during assembly. Subsequently, the ends of the outer sleeve can be formed in order to fix the spring body and the supporting structure in the outer sleeve against slipping out.The spring body is formed from an elastomeric material. It encloses the bearing core at least in regions. It is also conceivable for the spring body to enclose the bearing core in the entire region. In this case, the spring body can be vulcanized onto the bearing core.The support structure forms a support structure for the spring body. For this purpose, it has a first support ring and a second support ring. With the aid of the support rings, the spring body is held in the outer sleeve. For this purpose, the support rings are each arranged on the end face in the outer sleeve. The support rings can be fixed to the outer sleeve by means of end-face forming of the outer sleeve, for example by means of flanging or rolling, and in this respect can be connected to the outer sleeve in a form-fitting manner. It is also conceivable that the support rings can be fixed to the outer sleeve by means of welding and can thus be connected in a materially integral manner. Corresponding seals can be formed on the support rings, which seals bring about a seal between the support rings and the outer sleeve. These seals can be vulcanized onto the outer side of the support rings, for example.The support structure further comprises two half shells which are arranged between the support rings. The half shells are arranged at least partially in a form-fitting manner in the axial direction between the support rings and support these in the axial direction against bending or slipping in the direction of the bushing inward. Thus, they remain in the correct position within the outer sleeve. The half shells have essentially a basic shape which corresponds to a half or cut hollow cylinder. Its outer shape follows substantially the inner shape of the outer sleeve. In this case, it can have channels and ribs on the outside and / or on the inside. The two half shells can be placed against one another in such a way that they together form a likewise substantially hollow-cylindrical basic shape. Each of the half shells has a first and a second front side, which are each aligned in the axial direction toward the first or the second support ring. The front sides bear at least partially against the support rings in each case, so that a force flow in the axial direction between the two support rings can be formed by means of the half shells. Furthermore, each of the half shells has a first and a second end side, which face each other in the circumferential direction and are clamped in an axial direction. The end faces of the first half shell are directly opposite one another and can also touch one another at least partially.The spring body can have different structural elements. For example, it can have two annular membranes which, in the assembled state, delimit the end face of the hydraulic bearing in a sealing manner. For example, the two annular membranes can be vulcanized onto the support rings.Moreover, the spring body may have a stopper structure. The stopper structure may form, for example, a stop buffer for limiting radial movements of the bearing core within the bearing. In addition, the spring body has at least one intermediate membrane. The intermediate membrane is positioned, clamped and largely fixed in the radial direction with the aid of the support structure formed by the support rings and half shells, in particular with the aid of the half shells.At least two fluid chambers are formed within the bearing. Each of the fluid chambers is substantially bounded by the outer sleeve and the spring body. Parts of the supporting structure can also contribute to the delimitation of the fluid chambers. The intermediate diaphragms of the spring body separate the first fluid chamber from the second fluid chamber. During movements, in particular dynamic movements of the bearing core connected to the spring body relative to the outer sleeve, the intermediate membrane can be oscillated and stretched. The fluid disposed in the fluid chambers dampens the vibration.It is particularly advantageous that the intermediate membrane has a membrane head which is fixed in a receptacle which is formed by the end faces of the half shells. The intermediate membrane is thus reliably clamped between the bearing core and the outer sleeve and is held in position against inward slipping out and slipping in the circumferential direction. No vulcanizing on the radially outward side of the intermediate membrane on another component, for example a web of a support cage, is necessary. At the same time, it is possible in this way to realize a relatively long intermediate membrane. In other words: it is favorable if the half shells together form a positive-locking geometry on their end faces, in which geometry the outer-circumferential edge of the membrane head is fixed.It is advantageous in this case if the maximum thickness of the membrane head is greater than the maximum thickness of the intermediate membrane. In this way, the diaphragm head can form with the receptacle an undercut radially inward and can thus be fixed there against slipping out. At the same time, the intermediate membrane can be configured to be relatively thin and therefore flexible and stretchable. A thin intermediate membrane also has a low extensional stiffness, which contributes to a low overall dynamic stiffness of the bearing and thus to good acoustic properties of the bearing. The membrane head acts in this respect as an anchoring element for the intermediate membrane. The receptacle in which the membrane head is held can have a projection against which the base of the membrane head rests in the idle state. For example, it is conceivable that the receptacle is formed in that the two half shells have a profile along their end face, by means of which they are at a greater or lesser distance from one another when they are placed one against the other in accordance with the description above. This profile can be designed in such a way that, in the assembled state, viewed from the inside to the outside in the radial direction, a first region is initially formed in which the distance between the two half shells is only slightly greater than the intermediate membrane. This region can also be referred to as a membrane sheath. This region is narrower than the widest point of the membrane head. This first region is then followed by a region whose shape and size correspond approximately to the shape and size of the membrane head. In this region, the membrane head is inserted in the assembled state. This region can also be referred to as a diaphragm head receptacle.In a preferred embodiment variant, it is provided that the membrane head is movable in relation to the outer sleeve. For example, the membrane head can have a certain clearance in the membrane head receptacle, so that it can follow a movement of the intermediate membrane, in particular of the intermediate membrane in the membrane sheath. In particular, the membrane head can react to movements of the bearing core and / or movements due to the bulge of the intermediate membrane, wherein the movements of the intermediate membrane are transmitted through the membrane sheath to the membrane head. In this case, the receptacle has a slight play with respect to the membrane head in the lateral direction, that is to say in the circumferential direction, so that the membrane head can move easily, for example in a radial direction.In one embodiment variant, it is conceivable that of the at least two fluid chambers, at least the first fluid chamber and the second fluid chamber are fluidically conductively coupled by means of an overpressure channel. At least one valve is arranged in the fluid channel. Such coupling may allow pressure equalization between the fluid chambers. For example, a corresponding channel geometry can be formed in the half shells, which forms at least a part of such a fluid channel.In a further embodiment variant, it is conceivable that the receptacle and the membrane head together with the outer sleeve form a valve. This valve can, for example, regulate the opening of the fluid channel described above. The valve can be closed when the bearing core and thus the spring body, the intermediate diaphragm and the diaphragm head are in a rest position. If the bearing core then vibrates, the intermediate membrane initially expands only and the fluid in the two fluid chambers is subjected to a slight pressure. However, if the vibration then becomes stronger, the overpressure in one of the two fluid chambers becomes greater. At the same time, the amplified movement of the intermediate membrane also exerts a radial force on the membrane head, which leads to the membrane head being moved in the receptacle. This movement of the membrane head in the receptacle results in an opening of the valve and thus in an opening of the fluid channel, which can therefore also be referred to as an overpressure channel. As a result, the overpressure channel enables pressure equalization between the two fluid chambers.It is particularly favorable in this case if the receptacle forms a valve seat. The profile of the receptacle can have a region which guides the membrane head in a radially outward direction in such a way that it rests in a reproducible sealing manner on the inner wall of the outer sleeve in the idle state. In this respect, it can also be seen that it can also be advantageous if the membrane head forms or has a valve closure element. The valve closure element can have a valve base and a valve tip. The valve base is formed, for example, by that part of the membrane head which is adjoined by the intermediate membrane. The valve tip can be that part of the membrane head which, as described above, protrudes through the receptacle, sealingly abuts the inner side of the outer sleeve and can close the fluid channel. It can be seen that the diaphragm head can be designed, for example, as a triangular profile, wherein the tip of the triangle effects the closure of the valve and the base of the triangle forms the valve base. It is also conceivable for the valve closure element to be round. In any case, it is favorable if the valve seat forms a stop for the valve closure element, in particular for the valve base. It can be seen in this respect that it is advantageous if the diaphragm head has a valve base which is movable in relation to the outer sleeve, wherein the valve closure element is arranged on the valve base.It is furthermore advantageous if the valve is designed in such a way that the opening of the valve is coupled to a movement of the intermediate diaphragm which results in a movement of the valve base with respect to the outer sleeve. In such a valve, the diaphragm head in the rest position thus blocks the overpressure channel, so that the two fluid chambers are not connected to one another via the overpressure channel. In this case, the valve closure element is arranged in the receptacle in such a way that it is movable in the radial direction when the intermediate diaphragm is pulled on account of bearing movements and / or on account of differential pressures. When the valve is opened, the two halves of the overpressure channel are connected to each other so that fluid can be exchanged between the fluid chambers. In other words, the valve closure element can be moved back and forth between a first position, in which an overpressure channel is closed, and a second position, in which the fluid channel is open. It can be seen that the described construction of the valve permits a large overall extension length for the intermediate diaphragm and at the same time a large open area for the valve. High pressure peaks can also be reduced in this way and no additional component is necessary.In a preferred embodiment variant, it is provided that the hydraulic bearing has at least two valve seats and valve closure elements. It is advantageous if the two valve seats and valve closure elements are diametrically opposite one another.In any case, it is also conceivable for the spring core to form a stop stopper at least in the region of the fluid chambers in the radial direction. The movement of the bearing core in the radial direction can be limited in this way. The stop stopper can be located, for example, on the inner wall of the half shells.Overall, it can be seen that, in the case of a corresponding hydraulic bearing, a movement of the bearing core in relation to the outer sleeve leads to a movement of the intermediate diaphragm. The intermediate membrane is part of the elastomer body. The elastomer body is vulcanized onto the core and onto the support rings and forms the outer membranes between the core and the support rings. The membrane head is preferably radially movable. If a valve is formed, the diaphragm head opens up the passage of the valve seat at high differential pressures between the fluid chambers due to highly dynamic movement of the bearing in the hydraulic working direction, so that the two fluid chambers are connected to one another via the overpressure channel and a pressure equalization state can occur. Bulging of the diaphragm causes the valve closure element to also be pulled back radially and thus opened.Further features, details and advantages of the invention are evident from the wording of the claims and from the following description of exemplary embodiments on the basis of the drawings. The following are shown: FIG. 1 shows a schematic longitudinal section through an exemplary embodiment of a hydraulic bearing FIG. 2 ashows a schematic cross section through the exemplary embodiment of FIG. 1, in which the bearing core is in the rest position FIG. 2 b shows a schematic cross section through the exemplary embodiment of FIG. 1, in which the bearing core has dynamically moved into the maximally deflected right position FIG. 3 shows a schematic cross section through a further exemplary embodiment of a hydraulic bearingFIG. 1 shows a hydraulic bearing 10 having an outer sleeve 20, a bearing core 30, a spring body 40 and a supporting structure 50. The outer sleeve 20 has a first end face 21, a second end face 22, an outer side 23 and an inner side 24. The outer sleeve 20 accommodates all other components. The bearing core 30 is disposed inside the outer sleeve 20. The bearing core 30 has a recess 31 into which a fastening element can be inserted. The spring body 40 is made entirely or partially of an elastomeric material. The spring body 40 is arranged between the bearing core 30 and the outer sleeve 20. The support structure 50 has a first support ring 51, a second support ring 52, a first half shell 53 and a second half shell 54. The first support ring 51 has a collar 511. The collar 511 is supported on the end face on the first end face 21 of the outer sleeve 20. The second support ring 52 has a latching element 521. The latching element 521 engages behind the second end face 22 of the outer sleeve 20. Furthermore, both the first support ring 51 and the second support ring 52 have an outer side 513, 523 and an inner side 514, 524, respectively. The outer sides 514, 524 of the support rings 51, 52 each bear against the inner side of the outer sleeve 20. The seals 512, 522 are each disposed in grooves between the outer side 513, 523 of the support rings 51, 52 and the inner side 24 of the outer sleeve 20. The inner sides 513, 523 of the support rings 51, 52 are in contact with the spring body 40.The half shells 53, 54 of the supporting structure 50 are arranged between the supporting rings 51, 52. Each half shell 53, 54 has a first front side 531, 541 and a second front side 532, 542. It can be seen in FIG. 1 that the first front sides 531, 541 of the half shells 53, 54 each bear against the first support ring 51 and that the second front sides 532, 542 each bear against the second support ring 52. The half shells 53, 54 can in this way keep the support rings 51, 52 at a distance in the axial direction x. The half shells 53, 54 also each have an outer side 535, 545 and an inner side 536, 546. The outer sides 535, 545 face the inner side 24 of the outer sleeve 20. The outer side 535, 545 of the half shells can be in direct contact with the inner side 24 of the outer sleeve 20. However, a certain distance can also be formed between the inner side 24 of the outer sleeve 20 and the outer side 535, 545 of the half shells 53, 54. Thus, the half shells 53, 54 can have a channel geometry 55.It can also be seen in FIG. 1 that the spring body 40 has a first annular diaphragm 44, a second annular diaphragm 45 and a stop stopper 43. The diaphragms 44, 45 are in each case those parts of the spring body 40 which are in contact with the inner sides 513, 523 of the supporting rings 51, 52. For example, the membranes 44, 45 can be vulcanized onto the support rings 51, 52. In addition, the diaphragms delimit the fluid chambers 61, 62 in the axial direction X. The stop stopper 43 is formed in the region of the half shells 53, 54 and extends in a radial direction Z, which is formed perpendicularly to the axial direction x and represents the hydraulic working direction of the bearing. If the bearing core 30 oscillates in this radial direction Z, the spring body 40 oscillates with it, and the stop stopper 43 can find a stop on the inner side 536, 546 of the half shells 53, 54. The stopper stopper 43 can thus constitute a limit for the movement of the bearing core 30 in the radial direction Z.It can also be seen in FIG. 1 that the hydraulic bearing 10 has a first fluid chamber 61 and a second fluid chamber 62 in the region of the half shells 53, 54. The fluid chambers 61, 62 are each formed between the spring body 40 and the inner side 24 of the outer sleeve 20 and / or the half shells 53, 54. The fluid chambers 61, 62 are filled with a fluid 60. The fluid 60 suppresses the vibration of the bearing core 30 in the radial direction Z.It can be seen in FIGS. 2 a, 2 band 3 that the spring body 40 has at least one, preferably two, intermediate membranes 41. Each intermediate diaphragm 41 extends in a second radial direction Y from the bearing core 30 to the inner side 24 of the outer sleeve 20. In any case, however, the first radial direction Z and the second radial direction Y span a plane on which the axial direction X is perpendicular.It can also be seen in FIGS. 2 a, 2 band 3 that the intermediate membrane 41 has a membrane head 42. The diaphragm head 42 is fixed in a receptacle 70. The receptacle 70 is formed by two end faces 533, 543, 534, 544 of the half shells 53, 54. It can be seen that the end faces 533, 543, 534, 544 each have a profile which has at least a first region 71 and a second region 72. In the first region 71, the profile is shaped in such a way that the mutually opposite end faces, for example the end faces 533, 543 or the end faces 534, 544, are closer to one another than in the second region 72. In particular, the receptacle 70 in the first region 71 is shaped in such a way that the free space formed between the respectively opposite end faces 533, 543, 534, 544 has a thickness which substantially corresponds to the thickness Dm of the intermediate membrane 41. This region forms the membrane sheath. It can be seen in FIGS. 2 a, 2 band 3 that the diaphragm head 42 has a thickness Dkwhich is greater than the thickness Dmof the intermediate diaphragm 41; this thickness Dkcorresponds to the second region 72 of the receptacle 70. the second region 72 of the receptacle 70 is shaped in such a way that it can receive the diaphragm head 42 with or without play. In this case, the membrane head 42 is held in the receptacle 70 in each case by the constriction of the membrane sheath formed by the first region 71. It can be seen that the membrane head 42 is held in the receptacle 70 in a positive-locking manner. In the exemplary embodiment shown in FIG. 3, the diaphragm head 42 has little to no play in the receptacle 70; in the exemplary embodiment shown in FIGS. 2 aand 2 b, on the other hand, the diaphragm head 42 has a certain play.It can also be seen in FIGS. 2 aand 2 bthat the receptacle 70 has a third region 73. This third region 73 is shaped and dimensioned such that the tip of the membrane head 42 can project through the region 73 and the membrane head is directed into the sealing position. In the rest position of the bearing and under only slight load, the diaphragm head 42 then rests with its tip, which forms the valve closure element 421, against the inner wall 24 of the outer sleeve 20. It can also be seen in FIGS. 2 aand 2 bthat a fluid channel 63 is formed between the first fluid chamber 61 and the second fluid chamber 62. This fluid channel 63 can be closed by the membrane head 42. For this purpose, the diaphragm head 42 and the receptacle 70 form a valve. The receptacle 70 forms the valve seat. The diaphragm head 42 has a base 422 forming the valve base. The tip of the diaphragm head 42 forms the valve closing member 421.In FIG. 2 a, the hydraulic bearing 10 is shown in the rest position. The diaphragm head 42 closes the fluid channel 63. the intermediate diaphragm 41 is clamped between the bearing core 30 and the diaphragm head 42. In FIG. 2 b, the bearing core 30 is dynamically deflected in the radial direction z. It can be seen that the stop stopper 43 limits the movement of the bearing core 30 in the radial direction z, wherein the stop stopper 43 finds a stop on the inner side 546 of the half shell 54. It is of course also conceivable for the movement to take place in the opposite direction, i.e. for the stop stopper to find a stop on the inner side 536 of the opposite half shell 53. It can also be seen that the movement of the bearing core 30 stretches the intermediate membrane 41 and, due to the pressure difference between the two fluid chambers 61, 62, the intermediate membrane is bulged counter to the direction of movement. As a result, the diaphragm head 42 is moved in the receptacle 70. In this case, it is moved radially inward at least to such an extent that the valve closure element 421, that is to say the tip of the diaphragm head 42, at least partially opens up the overpressure channel 63. The valve closure element 421 therefore no longer sealingly abuts the inner side 24 of the outer sleeve 20. As a result, a large pressure relief valve cross section becomes free, so that the fluid 60 can flow from the one fluid chamber 62 into the other fluid chamber 61 via the pressure passage 63 and the pressure peak in the fluid chamber 62 can thus be reduced.The invention is not limited to one of the above-described embodiments, but can be modified in many ways.It is thus conceivable, for example, for the membrane head 42 also to have a round or polygonal shape. The number of fluid chambers can also vary. It is also conceivable for two fluid chambers 61, 62 to be present, wherein a first intermediate membrane 41 is fixed with its membrane head 42 as shown in FIG. 3, while a second intermediate membrane 41 is fixed with its membrane head 42 as shown in FIGS. 2 aand 2 b in a valve. In this case, these two intermediate membranes 41 can extend upwards once from the bearing core 30 in the radial direction Y and downwards once in the radial direction Y, as shown in FIGS. 2 a, 2 band 3.In any case, it is in the case of a hydraulic bearing 10, in particular in the case of a radially damping hydraulic bearing, having a bearing core 30, an outer sleeve 20 and having a spring body 40 made of elastomer material, which surrounds the bearing core 30 in a materially bonded manner at least in regions and is arranged between the bearing core 30 and the outer sleeve 20, wherein the hydraulic bearing 10 additionally has a supporting structure 50, which is formed by a first supporting ring 51 and a second supporting ring 52, and by two half shells 53, 54 arranged between the first and second supporting rings 51, 52, and which is arranged between the outer sleeve 20 and the spring body 40, wherein the hydraulic bearing 10 has at least one first fluid chamber 61 and one second fluid chamber 62, which are arranged between the spring body 40, the core, the supporting structure 50 and / or the outer sleeve 20, wherein the spring body 40 has at least one intermediate diaphragm 41, The diaphragm head is arranged between the first and the second fluid chamber 61, 62, and is advantageously provided with an intermediate diaphragm 41 with a diaphragm head 42 by means of which it is fixed to the supporting structure 50, namely in such a way that the diaphragm head 42 is arranged with or without play in a positive fit in a receptacle 70 which is formed by the half shells 53, 54. It is favorable if the maximum thickness Dk of the membrane head 42 is greater than the maximum thickness Dm of the intermediate membrane 41.In addition, it can be provided that the membrane head 42 is movable in relation to the outer sleeve 20. This is advantageous in particular when at least the first fluid chamber 61 and the second fluid chamber 62 of the at least two fluid chambers 61, 62 are fluidically conductively coupled by means of an overpressure channel 63. In this case, it is also particularly advantageous if the receptacle 70 and the membrane head 42 together with the outer sleeve 20 form a valve. The receptacle 70 can form a valve seat and the diaphragm head 42 can form or have a valve closure element 421. It is conceivable, for example, for the diaphragm head 42 to have a valve base 422 which is movable in relation to the outer sleeve 20, wherein the valve closure element 421 is arranged on the valve base 422. In any case, the valve is then configured such that the opening of the valve is coupled to a movement of the intermediate diaphragm 41 which results in a movement of the valve base 422 relative to the outer sleeve 20. In a preferred embodiment, the hydraulic bearing 10 has at least two valve seats and valve closure elements.It can also be provided in any case that the spring core 40 forms a stop stopper 43 at least in the region of the fluid chambers 61, 62 in the radial direction Z.All features and advantages which emerge from the claims, the description and the drawing, including structural details, spatial arrangements and method steps, can be essential to the invention both individually and in a wide variety of combinations.List of reference charactersA-A Sectional plane B-B Sectional plane Dm Thickness Dk Thickness X Axial direction Y Second radial direction Z First radial direction 10 Hydraulic bearing 20 Outer sleeve 21 End face 22 End face 23 Outer face 24 Inner face 30 Bearing core 31 Receptacle 40 Spring body 41 Intermediate membrane 42 Membrane head 421 Valve closure element 422 Valve base 43 Stop stopper 44 Membrane 45 Membrane 50 Support structure 51 Support ring 511 Collar 512 Seal 513 Outer face 514 Inner face 52 Support ring 521 Latching element 522 Seal 523 Outer face 524 Inner face 53 Half shell 531 Front face 532 Front face 533 End face 534 End face 535 Outer face 536 Inner face 54 Half shell 541 Front face 543 End face 544 End face 545 Outer face 546 Inner face 55 Channel geometry 60 Fluid 61 Fluid chamber 62 Fluid chamber 63 Overpressure channel 631 Closure point 70 Receptacle 71 first region 72 second region 73 third region 74 surface

Claims

Hydraulic bearing (10), in particular a radially damping hydraulic bearing, having a bearing core (30), an outer sleeve (20) and having a spring body (40) made of elastomer material, which spring body comprises the bearing core (30) in a materially bonded manner at least in regions and is arranged between the bearing core (30) and the outer sleeve (20), wherein the hydraulic bearing (10) additionally has a supporting structure (50) which is formed by a first supporting ring (51) and a second supporting ring (52), and by two half shells (53, 54) arranged between the first and second supporting rings (51, 52), wherein the hydraulic bearing (10) has at least one first fluid chamber (61) and one second fluid chamber (62) which are bounded by the spring body (40), the half shells (53, 54) and / or the outer sleeve (20) and the bearing core (30), wherein the spring body (40) has at least one intermediate membrane (41), A diaphragm which is arranged between the first and the second fluid chamber (61, 62), wherein the at least one intermediate diaphragm (41) has a diaphragm head (42), with the aid of which it is fixed to the supporting structure (50), to be precise in such a way that the diaphragm head (42) is arranged in a positively locking manner, with or without play, in a receptacle (70) which is formed by the half shells (53, 54), characterized in that the maximum thickness (Dk) of the diaphragm head (42) is greater than the maximum thickness (Dm) of the intermediate diaphragm (41).Hydraulic bearing according to Claim 1, characterized in that, of the at least two fluid chambers (61, 62), at least the first fluid chamber (61) and the second fluid chamber (62) are coupled in a fluidically conductive manner by means of an overpressure duct (63).Hydraulic bearing according to one of the preceding claims, characterized in that the receptacle (70) and the diaphragm head (42) together with the outer sleeve (20) form a valve.Hydraulic bearing according to Claim 3, characterized in that the receptacle (70) forms a valve seat.Hydraulic bearing according to either of Claims 3 and 4, characterized in that the diaphragm head (42) forms or has a valve closure element (421).Hydraulic bearing according to one of Claims 3 to 5, characterized in that the diaphragm head (42) has a valve base (422) which is movable in relation to the outer sleeve (20), the valve closure element (421) being arranged on the valve base (422).Hydraulic bearing according to one of Claims 3 to 8, characterized in that the valve is designed in such a way that the opening of the valve is coupled to a movement of the intermediate diaphragm (41) which results in a movement of the valve base (422) with respect to the outer sleeve (20).Hydraulic bearing according to one of the preceding claims, characterized in that the hydraulic bearing (10) has at least two valve seats and valve closure elements.Hydraulic bearing according to one of the preceding claims, characterized in that the spring core (40) forms a stop stopper (43) at least in the region of the fluid chambers (61, 62) in the radial direction (Z).

Images